Ironing machine drive mechanism



Aug. 21, 1951 w. H. BRADLEY IRONING MACHINE DRIVE MECHANISM 5 Sheets-Sheet 1 Filed June 16, 1944 fnven/or iZZiamfiBradZg Aug. 21, 1951 w. H. BRADLEY IRONING MACHINE DRIVE MECHANISM 5 Sheets-Sheet 2 Filed June 16, 1944 'IIIIII III- jiwelzzfiar' WilliamfiB radlg BY fil /077236- Aug. 21, 1951 w. H. BRADLEY IRONING MACHINE DRIVE MECHANISM 5 Sheets-Sheet 5 Filed June 16, 1944 [i2 verzzor fiBradZg l l I I l lllkll lyillilil v QM mm m f mm W m% n% h Z W l 2% W 3 A l I I 9 l m r I T R .R R Q M w G wm m: v hm nmW Hm no, 0 t, a x QT i 3% 1 ll 8 w mm P h mm Hhl. I 58 m3 I. w b F ,.I \N b8 N\\ hm. 5w 8Q Aug. 21, 1951 w, H. BRADLEY 2,565,199

IRONING MACHINE DRIVE MECHANISM Filed June 16, 1944 5 Sheets-Sheet 4 IZI fiwenzor' WzZZzaig iBradlg f gumm filonz ys.

Aug. 21, 1951 Filed June 16, 1944 flllllllllllllllllill lmlllll I 1 I w. H. BRADLEY IRONING MACHINE DRIVE MECHANISM 5 Sheets-Sheet 5 Invenior wz/llzialggbradlg Patented Aug. 21, 1951 IRQNIN-G MACHINE DRIVE MECHANISM William Ii. Bradley, Fort Wayne, Ind., assignor to Horton Manufacturing Company,

Fort

Wayne, Ind., a corporation of Indiana Application June 16, 1944, Serial No. 540,672

24 Claims.

The invention relates generally to ironing machines and more particularly to an ironing machine having a pair of coacting ironing elements, one of which is a roll.

The general object of the invention is to provide a novel ironing machine having a pair of ironing elements, at least one of which is a roll, and one of which is movable toward and from the other by power actuated means driven by the motor for driving the roll, the machine being of such capacity as to be suitable for ordinary domes-tic use and having mechanism for shifting the movable element of such a character that a relatively small motor may be employed to serve both driving functions.

Another general object is to provide a novel ironing machine of the type having a pair of relatively shiftable ironing elements, one of which is a roll, and having power actuation of the shiftable element, the machine being so constructed that, although it has a capacity equal to that of much heavier machines, its total weight is such that it may be constructed in the form er a ortable machine.

Still another general object is to provide a novel ironing machine of the roll and shoe type, in which the major portion of the gearing for rotating the roll and shifting the shoe is located within the roll and is compactly constructed to occupy .a minimum of space.

further object is to provide an ironing mash iftable and ncn-shiitable ironing elements, one of which is .a roll, with a single motor for driving the roll and for moving the shiftable element, and with means serving to absorb energy when the shiftable element is moved away from the other element and to augment the drive of the motor by utilization of such energy when the shiftable'element is moved toward the other element.

.Still another object is to provide an ironing machine having shift-able and non-shiftable ironing elements, one of which is a roll, and motor driven means for effecting the shifting movement, the machine being provided with novel means of simple construction serving to absorb excess energy from the motor driven means during a portion of its operating cycle when the load thereon is relatively light and to return such energy to the motor driven means when the load thereon is at a peak.

A still furtherobj'ect is to provide an ironing machine having a pair of ironing elements, one shifitable toward the other and one of which is a motor driven. roll, :the machine having mechanism driven by the motor and including a cam operable to effect the shifting movement, which cam is constructed so that it may be operated at a relatively slow speed, thus permitting the motor to be of relatively small power rating.

Another object is to provide a clutch controlled drive for the above-mentioned cam, which clutch operates at a speed substantially higher than that of the cam so that the load on the clutch is thereby minimized and disengagement thereof may :be readily accomplished.

Still another object is to provide an ironing machine comprising a pair of relatively shiftable elements, and power operated mechanism for eiiecting the shifting movement including a clutch constructed in such a manner that it may be positively disengaged and cannot over-run, the clutch comprising engageable members which separate a sumcient distance when disengaged to avoid all chance of clicking against each other.

A still further object is to provide an ironing machine comprising a pair of relatively shiftable elements and power actuated means for effecting the shifting movement including a clutch so situated in said means that it requires one revolution to effect movement of the elements toward each other or from each other, thus necessitating but a single disengaging device, thereby sim- .plifying the structure.

It is also an object to provide an ironing machine comprising a pair of relatively shiftable elements, power actuated mechanism for effecting the shifting movement, and novel lever con nections between said mechanism and the shiit-' able element.

Another object is to provide a novel ironing machine comprising a relatively shiftable roll and shoe, with a power drive for rotating the roll and effecting the shifting movement including a roll clutch, said clutch being positively disengaged when the roll and shoe are separated, but being disengageable when the roll and shoe are engaged to permit pressing.

A further object is to provide an ironing machine comprising a pair of relatively shiftable elements, one of which is a roll, power actuated mechanism for effectin the shifting movement and for-driving the roll, and a control member adjustable into one position where it may be conveniently actuated by the operators knee, into another position for actuation by the 013-. erators elbow, or into a plurality of positions for manual action by the operator.

A still further object is to provide an ironing machine comprising a pair of relatively shift able elements, power actuated mechanism for effecting the shifting movement, and a shiftable control member normally adapted to be manually actuated but so contructed that a foot control device may be readily connected thereto.

Other objects and advantages will becomeapparent from the following description taken in connection with the accompanying drawings, in which:

Figure 1 is a front elevational view of an ironing machine embodying the features of the invention.

Figure 2 is an end elevational view of the machine.

Figure 2a is an enlarged fragmentary sectional view taken on the line Ear- 2a of Figure 1.

Figure 3 is an end elevational view on a larger scale with parts broken away to show the operating mechanism.

Figure 4 is a vertical sectional view taken longitudinally of the machine.

Figure 5 is a horizontal sectional View of the operating mechanism.

Figure 6 is a detail of the mechanism for shifting one of the ironing elements toward and from the other.

Figure '7 is a detail of the roll driving mechanism.

Figure 8 is a perspective View of another detail of the mechanism for shifting one of the elements toward and from the other.

Figure 9 is a diagrammatic view of the drive mechanism.

Figure 10 is a fragmentary face view of the actuating cam of the drive mechanism.

In ironing machines heretofore commercially manufactured, of the type provided with power actuation for the shiftable ironing element, the size of motor deemed necessary to operate such a machine has been so large that such machines had considerable weight. Such machines as heretofore constructed, usually employed an eccentric or its equivalent to eiiect the shifting movement of the one element toward and from the other. The two ironing elements were resiliently urged toward each other when in operative relation, and the power operated mechanism not only had to carry the load required to shift the one element toward the other, but also was subjected to an additional load incurred in placing the resilient means under pressure.

When the one element was shifted away from the other, the power operated mechanism was subjected to a much lighter load, since then no power was required to place the resilient means under pressure, and also because the resilient means tended to force the elements apart and thereby assisted the motor. The motor was thus subjected to a peak load when moving the one element toward the other, and a much lesser load was placed upon it when the one element was moved away from the other.

Such a construction involved other problems which brought about an increased motor load. Thus since the load in shifting the one element away from the other was much less than the load in shifting the load in the opposite direction, there was a tendency to cause the clutch in the power mechanism, which connected the power drive with the shifting means, to over-run if it were not provided with a positive stop. Even if the positive stop were provided, the clutch was subjected to such difierent loads for the two directions of movement of the shifting element that it would not operate satisfactorily. To overcome these difficulties, the mechanism was frequently provided with a brake to stop the driven parts as soon as the clutch was disengaged. Such a brake, which in many machines acted throughout the complete cycle of operation, consequently increased the motor load still more. In fact, such a brake has been found in some commerically manufactured machines to have increased the motor' load as much as 50%.

Under such conditions a relatively large motor was required, although only a small part of the power thereof was actually utilized for the purpose of shifting the one element. The balance of the power was thus spent in overcoming the difficulties in construction of the machine rather than for performing a useful function.

Other factors were also present in many such machines, which necessitated a relatively large motor. Thus the eccentric or cam driving member in the power mechanism for effecting the shifting movement usually had to be driven through at least a half revolution to efiect movement of the one element in one direction. If this movement was to be accomplished at not too slow a speed, the load on the motor was much greater than if the driving member could have been driven through a smaller part of a revolution to effect the same movement. Also, in many machines the drive from the motor to the roll was not disconnected until after, or at least near the end of, the shifting movement of the one element, so that the motor was thus carrying both loads at the same time. Furthermore, the drive from the motor to the roll was disconnected by a clutch, usually located near or on the roll shaft so that even when such clutch was disenaged the motor continued to drive the reduction gearing connecting the clutch with the motor.

The relatively large size of motor necessitated by these circumstances affected the design or construction of the machine in several material respects. Thus it added substantially to the weight of the machine as a whole, so much so in fact that a machine could not be built within a weight range deemed proper for portable type machines, if the machine were to have a practicable ironing capacity. The weight of the motor also controlled the position in which it could be mounted in the machine and the manner of supporting it. The large motor also added materially to the cost of the machine as well as the cost of operation.

General descr ption of the machine As shown in the drawings, the machine comprises, generally, a base 20 which in the present instance is of the type adapted to be placed on a table or the like. While the machine shown herein is of the so-called portable type, it is to be distinctly understood that the invention is not limited to a machine of this particular type but can be embodied in machines of other types. At one end of the base is a vertically extending head 2| which, in the present instance, is at the right end of the machine as is customary. Supported from the head 2| is a roll 22 constituting one of the cooperating ironing elements. The roll 22 is positioned with its axis horizontal and extending parallel to the front of the base 20. The other ironing element in the present instance is a shoe 23 mounted at the rear of the roll 22.

The two ironing elements, namely, the roll 22 and the shoe 23, are relatively shiftable toward and from each other to permit the insertion sesame therebetween of an article to be ironed and to permit the withdrawal of such an article. To effect such movement, the shoe in the present instance is shiftable, and for such purposes the shoe is provided on its rear'side with a pair of rearwardly extending ears 24 pivotally connected by a pin 25 (see Figs. 2 and 3) to an upstanding arm 26 extending from the base at a point substantially midway between the ends of the roll 22. The arm 26 is pivotally supported to swing the shoe 23 toward and from the roll, and for this purpose is rotatably mounted on a rock shaft 21 located within the base 20 and extending from the arm 25 toward the head 2|.

To effect the shifting movement of the shoe, the'shaft 21 has rigidly secured thereto a lever 30 which, in the present instance, extends upwardly and is encased by the arm 26. The lever 30' is substantially shorter than the arm 26 and pivotally supports at its upper end a toggle device comprising toggle members 3| and 32, the latter slidably extending through the in 25 on which the shoe is supported. The toggle member 32 is in the form of a screw having a nut 33 threaded thereon and a spring 34 hearing against the nut at its lower end and against the pin 25 at its upper end. The toggle members 3| and 32 are normally held in an extended position so that swinging movement of the shaft 2'! and lever 3|] causes the arm 26 to shift the shoe toward the roll 22. The toggle members 3| and 32 constitute a means for releasing the shoe from the roll in case of emergency, and to this end the lower toggle member 3| is provided with an upstanding hand lever 35 by which the toggle may be broken to permit the arm 25 to swing rearwardly from the roll.

The spring 34 also serves the function of resiliently forcing the shoe toward the roll when the shoe and roll are in cooperating relation. Such and when the shaft 27 is rocked in a direction,

to move the shoe away from the roll, the position of the shaft is such that the weight of the shoe and its supporting structure are at the rear side of the axis of the shaft 21 and thus holds the shoe in its position remote from the roll. To prevent the shoe from swinging downwardly about the pin 25 when moved. away from the roll, an abutment or seat 36 is provided on the arm 26 against which the shoe may rest when not in use. The shaft 2'! is adapted to be rocked to effect the movement of the shoe by means of a curved lever 37 rigidly secured to the end of the shaft 21 adjacent the head 2|. The lever 3"! is shaped to extend forwardly within the base 20 and thence upwardly into the head 2 I. Within the head 2|, the free end of the lever 3'5 is connected to mechanism by which the shoe may be shifted by the power drive of the machine.

The r011 22 is of the usual padded and cloth covered type, and in this instance is positioned so that it telescopes for a short distance over a 'portion of the head 2!, as shown in Figs. land-4.

While the roll may have any desired construe tion, in the present instance it comprises a cylin' dri'cal sheet metal tube 40 rigidly mounted on a plurality of sheet metal dished members 4|, one of which is shown in Fig. 4. The dished members are preferably positioned inwardly from the ends of the roll and are carried on and rigidly secured to a roll shaft 42. The roll shaft 42 extends from and is journalled in an extended portion 43 of a gear casing 44 supported by the head 2!. The gear casing 44 is thus concealed from view by being located within the roll 22.

The gear casing 44 is provided with a cover portion 45, and a motor 46, by which the machine is driven, is mounted on the cover 45. The gear casing and cover are so positioned that a portion of the cover 45 extends into the upper part of the head 2| to locate the motor 46 therein. The motor 46 carries a fan 41 located within the head 2' I and adapted to draw air into the head through louvers 5!] formed in the head casting. The fan thus forces the air around the motor and the gear casing and outwardly through the roll 22.

To simplify the construction and assembly of the gear casing 44, its cover 45, and the head 2|, the gear casing and its cover are secured together by bolts 5| which likewise secure the assembled casing and cover to the head 2|.

The motor 45 is adapted to drive mechanism carried principally within the gear casing 44 for rotatably driving the roll and for effecting shifting movement of the shoe under the control of the operator. The motor thus serves this double function and is subjected to the individual loads incurred in performing each of these functions.

The roll drive Since the motor 46 operates at a relatively high speed and it is desired to have the roll 22 operate at a much slower speed, reduction gearing is provided between the motor and the roll shaft 42. It is likewise desirable to stop the rotation of the roll whenever the shoe is moved out of cooperative relation therewith. For this purpose, a clutch is provided in the gearing. While the clutch has heretofore usually been placed at such cent to the roll shaft, such a position is undesirable when the load on the motor is considered,

since the major portion of the gearing extended between the clutch and the motor and continued to be driven even after the clutch was disengaged.

In the present instance, a material reduction in the load placed on the motor by the constantly driven parts of the roll drive gearing is effected by placing the clutch at a point nearer the motor in the gear train than has heretofore been the usual practice. Thus the number of parts that are constantly driven by the motor when the roll is disengaged is reduced and the frictional load thereof on the motor is materially lessened. A further advantage accrues from this construction since the motor clutch when so placed in the gear train is obviously operating at a higher speed and a lesser load, and may therefore be engaged and disengagedwith a much more sensitive control than if it were operating at a slower speed and higher load.

in the present instance, the gearing for driving the roll comprises a pinion 52 (see Figs. 3, 5 and 9) mounted on the motor shaft and meshing with a gear 53 carried on a drive shaft 54. The drive shaft 54 is journalled at its right-hand end in the gear casing cover 45 and at its left-hand end in the gear casing 44. The drive shaft "54 carries a pinion 55 adjacent its left end, meshing with a constantly rotating gear 53 rotatably mounted on a stub shaft 51.

- The stub shaft is likewise journalled at one end in the gear casing cover 45 and at its other end in the gear casing 44 and carries a clutch, indicated generally at 50 for connecting the gear 56 in driving relation with the stub shaft 51. The stub shaft 5'! has rigidly secured thereto a pinion 8i meshing with a gear 52 carried on the right-hand end of the roll shaft 42 within the gear casing 44. The clutch 55 is thus so located in the gear train between the motor 46 and the roll shaft 42 that when disconnected it permits a substantial part of this gear train to stop its rotation, and the frictional load placed on the motor by those parts which are constantly driven will thereby be materially reduced. Specifically, it will be noted that when the clutch '50 is disengaged, the gear 52, the pinion 5|, as well as the stub shaft 57, will be disengaged from the drive and may stop. The only parts of this train that are constantly driven are the gear 56, pinion 55, drive shaft 54 and gear 53. It is necessary, however, to constantly operate the drive shaft 54 since, as will be later described, this shaft also drives the mechanism for effecting the shifting movement of the shoe. However, the reduction of the frictional load on the motor in the present arrangement of the roll drive gearing is substantially less than has been incurred by gearing commonly utilized heretofore in commercial machines.

Another advantage arising by virtue of placing the clutch in the position herein disclosed is that the clutch rotates at a relatively high speed when driving the roll and the clutch load is thereby materially lessened. The clutch therefore may be easily disengaged under load since the pressure of the load does not tend to hold the parts of the clutch in engagement to the extent that such parts would be held were the load heavier.

The clutch E8, in the present instance, comprises a shiftable member 53 (see Fig. '7) slidably mounted on the stub shaft 5? but secured for rotation therewith as by a key 64. The member 63 is provided with a flange 65 having a plurality of annularly arranged apertures 66 adapted to receive pins 61 rigidly mounted in and extending from the adjacent face of the constantly rotating gear 56. The projecting ends of the pins 51 are rounded so that they will cam themselves into the apertures 86, should they be out of alignment therewith when the flange 65 is moved toward the gear 55.

The shiftable clutch member 63 is adapted to be moved toward the gear 55 to effect engagement with the pins 51 by means of a coil spring 78 surrounding the stub shaft57 and abutting against a washer H held against endwise movement by a transverse pin 72. To effect disengagement of the clutch, the clutch member 63 is provided with a second flange '13 engageable by one arm of a bell crank 74. The bell crank i4 is adapted to be manually operated to disengage the clutch at certain times in the operation of the machine and also is adapted to be engaged by a portion of the shoe shifting mechanism, as will be more fully described hereinafter, to hold the clutch in its disengaged position when the shoe is moved away from the roll.

The bell crank 14 comprises a somewhat elongated web portion 15 (see Figs. 3, 4 and '7) bent at an angle to form the two arms of the bell crank and having at its two ends flange portions 16 87 which are pivotally supported by a bracket IT secured to the interior of the gear casing 44.

The shoe shifting mechanism As heretofore mentioned, the shoe 23 is adapted to be shifted by power supplied by the motor 45. Such mechanism is controlled by the operator and is adapted to shift the shoe in one direction or the other under the control of the operator, and to disengage the power drive from the mechanism automatically at the conclusion of the shifting movement.

In the present instance, the power for effecting the shifting movement is received from the drive shaft 54. Mounted on the shaft 54 adjacent its right end is a pinion constantly driving a gear 8! (see Figs. 3, 4, 5 and 9). The gear 8| is rotatably mounted on a shaft 82, and rigidly secured to the gear 81 is a peripherally notched driving member 83. The notched driving member 83 thus is constantly driven.

Rigidly secured on the shaft 82 is a driven member 84 in the form of a disk provided with a hub 85. The disk portion of the driven member 84 is closely adjacent the driving member 83 and is adapted to be connected therewith to effect engagement of the power drive for shifting the shoe. Such driving engagement is effected through a finger 86 carried by the driven member 84. When the driving and driven members 83 and 84 are in driving engagement, the shaft 82 is thereby rotated. The shaft 82 also carries a pinion 81 meshing with a gear 55 mounted on a cam supporting shaft 9 l. Mounted for rotation with the gear 90 is a cam 92 which, in the present instance, is of a form comprising a plurality of lobes 93 adapted to successively engage a cam follower or lever 94.

The cam follower or lever 94 has a rounded end portion 95 (see Figs. 3 and 8) adapted to bear against the periphery of the cam 92 so that the lever 94 will be actuated by rotation of the cam. The lever 94 is pivotally supported intermediate its ends on a tubular member 95 mounted in the gear casing cover 45. The lever 94 extends downwardly and at its lower end has a pin 97 extending therethrough for connecting the end of the lever 94 with the adjacent end of an intermediate lever l00. The lever I00 is mounted on and is secured to a rock shaft [01 journalled in the gear casing cover and extending therethrough. Secured to the outer end of the rock shaft IEJI is a second intermediate lever I82 pivotally connected by spaced links I83 to the free end of the shoe actuating lever 31.

By an inspection of Fig. 3, it will be noted that when the rounded end portion 95 of the lever 94 is in engagement with the high point of one of the lobes 93 of the cam 32, the arrangement of levers is such that the free end of the shoe actuating lever 31 is moved downwardly to move the shoe into operative relation with the roll, as shown in that figure. Further rotation of the cam will permit the rounded end portion 95 of the lever 94 to move inwardly toward the cam axis and thereby raise the free end of the lever 31 to permit the shoe to fall away from the roll. In the present instance the weight of the shoe and its support are such that they tend to move away from the roll and thus hold the rounded portion 95 of the lever 94 in engagement with the cam 92.

Since the cam lever 94 and the first intermediate lever IIJO are mounted on fixed pivots, the pin 91 which connects these two levers must be permitted to shift relative to one .of them to provide for the swinging movement of both of these levers about different axes. To this end, the pin 91 is fixed in one of the levers and operates in a slot in the other of these two levers. In the present instance the pin 91 is fixed to the upper end of the intermediate lever I and the slot, indicated at I04, is provided in the end of the cam lever 94. In order to equalize for both directions of movement the friction incurred in moving the pin 91 in the slot I04, the slot is elongated in a direction which is substantially transverse to the direction of movement of the pin. Thus the pin 91 bears perpendicularly against the side of the slot throughout its entire movement and will have I no uphill action for one direction or downhill action for the other direction of movement. The friction thus is uniform throughout the operating cycle.

The position of the'slot I04 also has another function in facilitating movement of the shoe toward and from the roll. In moving the shoe toward the roll the power required during the first part of the movement merely is that. necessary to effect the shifting movement of the shoe without any resistance offered to such movement other than the weight of the shoe. During the latter part of the movement, however, the spring 34 which resiliently urges the shoe toward the roll'has to be placed under compression so that the shoe will exert proper pressure against the articles being ironedwhen they pass between the roll and the shoe. A substantially greater load is therefore incurred during the latter part of the shoe movement because of the spring 34.

The slot I04 is therefore placed in such .a position that the effective leverage of the lever I65 is increased toward the end of the shoe movement toward the roll. Thus it will be noted by an inspection of Fig. 3 that the pin 91 is located at the outer end of the slot I04 when the shoe is in operative relation to the roll, and the effective leverage of the intermediate lever I60 is greater at that time and has just moved through that part of its movement which serves to effect compression of the spring 34. As the shoe moves away from the roll, the pin 91 moves to the left, as shown in Fig. 3, and will thence move downwardly or toward the inner end of the slot I64 to reduce the effective leverage of the intermediate lever I00. By this construction the maximum leverage for the lever I00 is attained at a time when the load, due to the spring 34, is the heaviest.

As heretofore mentioned, each lobe 9-3 of the cam 62 is adapted to effect a movement of the shoe toward the roll when the cam is moved through an angle equal to one half the angularity of each. lobe, and similarly is adapted to move the shoe away from the roll by an equal movement of the cam. Each lobe thus has a rising portion and a receding portion to effect such movement, the 'cam rotating in the direction indicated by the arrow in Fig. 3. The drive for the cam therefore must be stopped both at each low point as well as each high point, the low points being the position of contact with the rounded end 95 when the shoe is away from the roll and the high points being the point of contact with the rounded end 95 when the shoe is in operative relation with the roll.

In the present instance, the cam is provided with four lobes so that it has eight stopping points. In most commercial machines heretofore manufactured, an eccentric or a cam. having one high point and one low point was utilized. The cam in these former machines thus had to rotate through a half revolution to effect a shift of the shoe in either direction. In the present instance, the cam need be rotated only through one eighth of a revolution to effect the same movement of the shoe. The gearing connection of the cam with the motor, in the present instance, thus may effect a greater reduction in speed than the reduction required in former structures.

The slow speed of rotation of the cam, however, would place an unduly heavy load on a clutch for controlling the rotation of the cam, if the clutch were placed so that it was driven at the same speed as the cam. Such heavy load would require an extraordinarily strong force to effect disengagement of the cam and as a result control of the drive mechanism could not be sufficiently sensitive.

It is, therefore-desirable to place the clutch which controls the rotation of the cam at some point in the gearing for driving the cam which operates at a higher speed than the cam. Such point in the gearing is obviously closer to the motor and thus provides an additional advantage in the structure in that'it reduces the number of parts in this gear train that are constantly driven.

In thepresent instance the clutch, which is formed by the finger 86 and the notched driving member 83, is mounted on a different axis than the cam and the gear which drives the cam, and the gear 90 has an 8 to 1 ratio with the pinion 8! meshing therewith. The clutch being mounted on the same shaft with the pinion 81 rotates eight times as fast as the cam 92, and the load on the clutch. is thus materially decreased so that it maybe easily disengaged when under load.

The clutch for controlling the rotation of the cam 92, as mentioned above, comprises in the present instance the finger 86 and the notched driving member 83. The finger 86 is pivotally supported by a .pin I05 (see Fig. 6) extending from one face of the driven member 84, and is curved to extend about the driving member 83. Intermediate its ends the finger 86 is provided with a tooth I06, and the finger 86 is adapted to swing about the pin I05 to move the tooth I06 into engagement with one of the notches in the driving member 83 to thereby effect engagement of the clutch. Disengagement of the clutch, obviously, is effected by swinging the finger 86 outwardly to move the tooth I06 beyond the periphery of the driving member 83. Normally the finger 86 is urged in a direction to cause engagement with the tooth I06 and the driving member 83 by a spring. Such spring, indicated here at I-0'I, is of the torsion type and surrounds the pin I05, the spring being located between the adjacent faces of the finger 86 and the driven member 84. The spring I 0'! is provided with tangentially extending arms H0 and III, the arm IIO having its end hooked to engage in an aperture H2 in the driven member 84, and the arm III having its end hooked to engage in an aperture H3 in the end of the finger 86. The spring is so wound that through its arms .0 and III it exerts a force tending to pivot the finger 86 about the pin I05 to cause the tooth I06 to engage the driving member 86. When the tooth I06 is so engaged with the driving memher, the driven member 84 will thus rotate with the driving member 83.

The finger at its other or free end. indicated at I I4, extends beyond the periphery of the driven member 84 for engagement with a disengaging member, indicated generally at H5, movable into and out of the path of the end i M of the finger 85. When the disengaging member H5 lies in the path of the end H4, engagement of the end H4 therewith causes the finger 35 to swing about the pin I05 and thus move the tooth I06 out of engagement with the driving member 83. When the disengaging member H5 is shifted out of the path of the end H4, the spring I01 causes the tooth I06 to move into engagement with the driving member 83.

' The finger 85 provides a positive stop for the driven member 84 when the tooth I06 is disengaged from the driving member 83. Thus it will be noted that the end H4 of the finger 86 swings outwardly when being disengaged by the member H5, such outward swinging movement brings the end H4 more fully into engagement with the disengaging member II5 so that rotation of the finger 83 and the driven member 84 will thereby be positively stopped by the disengaging member H5. Such positive stop pre vents over-running of the clutch, and the shoe consequently will definitely be stopped in its shifting movement either in its roll engaging position or when moved away from the roll.

It will be noted that each notch in the driving member 83 has a straight rear side H6 so that the tooth I 06 will have positive engagement with the driving member during driving and cannot be forced out of such driving engagement. The forward side of the notch, however, is flared out-- wardly, as at I I1, away from the tooth to permit the tooth to move freely out of the notch when the finger 86 is swung about its pivot pin I05.

Because of the positive stopping of the driven member 84 by the disengaging member H5, such stoppage is apt to occur the moment that the tooth I06 barely clears the periphery of the driving member 83. Rotation of the driving member 03 relative to the tooth I06 is therefore apt to cause a clicking noise between the two unless the tooth I06 is moved a substantial distance from the driving member 83. The present structure is arranged to prevent such clicking noise by moving the finger 36 so that the tooth I06 is entirely clear of the driving member. To this end, the finger 83 is provided with an elongated slot I20 in which the pivot pin I05 is received, and the torsion spring I! is formed in a loop of substantially larger diameter than the pin I05. When the tooth I03 is in engagement with the driving member 83, as shown in Fig. 6, the torsion spring I0! first causes the finger to pivot counter clockwise about 'the pin I05. When the tooth M16 is fully engaged in the driving member 83, the pull of the driving member 83 tends to shift the finger 86 on the pivot pin I so that the latter will be positioned in the outer end of the slot I20, as shown in Fig. 6.

When the disengaging member H5 swings the finger 86 to disengage the tooth I 06 from the driving member, the movement of the finger 86 is first a pivotal movement about the pin I05. However, as soon as the tooth I06 is disengaged from the driving member, the torsion spring tends to swing the finger 86 about its end H4, and the finger will thus be shifted so that the pin I05 is at the inner end of the slot I20, the elonga tion of the slot being transverse to a line extending from the slot to the end II4. Such shifting movement of the finger about the end H4 moves the tooth I06 entirely clear of the driving mem- I2 ber 83 so that the former cannot click against the latter during relative rotation.

The disengaging member II 5 is loosely supported at its outer end for shifting movement by a rock shaft IZI extending through the tubular member 00, the rock shaft I2I being rotatable relative to the disengaging member H5 for purposes hereinafter described. The disengaging member I I5 is also loosely supported adjacent its finger engaging end'on an extension I22 of the cam supporting shaft 9 I. The disengaging member is adapted to be shifted with a slight tilting movement, due to its loose mounting, which movement is generally in a direction parallel to the axis of the driving member 83 and driven member 84 to move in and out of the path of the finger 85. Normally the disengaging member H5 is urged into such path by a compression spring I23 mounted on the extension I22 and is adapted to be momentarily shifted out of such path by control means, hereinafter described.

Reduction of motor load As heretofore mentioned, the load on the motor and driving mechanism, incurred when shifting the shoe away from the roll, differs considerably in prior machines from the load incurred on shifting the shoe toward the roll. Thus when the shoe is being shifted toward the roll, the load is due not only to the power required for moving the shoe but also for placing the spring 34, which urges the shoe toward the roll, under compression. In actual practice, it is found that the load incurred by compressing the spring 34 is considerably greater than the load incurred mere- 1y by shifting the shoe. On the other hand, when the shoe is moved away from the roll, the compression of the spring 34 tends to cause an overdrive in the shoe shifting mechanism, thus materially lessening the load. In other words, the spring 34 tends to oppose the motor when the shoe is moved inone direction and tends to assist the motor when the shoe is moved in the opposite direction.

Such effect of the spring 34 is so great that it would materially affect the size of motor used if it were not compensated form some manner. The tendency of the spring 34 to assist the motor during one direction of movement of the shoe could of course be overcome b applying a brak ing force to the mechanism during such time. But energy is lost by utilizing such a braking force if the braking action is provided by a brake of the friction or similar type. If a braking force is applied throughout the entire cycle as in many prior machines then. of course, the load on the motor is excessive, since the power required to overcome the braking force is in addition to the power required to shift the shoe and compress the spring.

The present invention provides means for effecting the desired braking action during the time when the spring 34 tends to assist the motor, and to store the energy expended in such braking action for return to the driving mechanism at the time when the load on the motor is greatest, that is, when the shoe is being moved toward the roll and the spring 34 is being placed under compression. To accomplish this purpose, I provide an energy storing device acting in the present instance on the cam 92 and functioning to store energy during the time when a receding portion of the cam is in cooperative relation with the cam lever 94. The energy storing device is also operable to return such energy to the mechanism by tending to drive the cam forwardly when with the lever 94. As shown in Figs. 3, 4 and 8, such energy storing device comprises a spring pressed member in the form of a plunger I24 slidably mounted in a socket I25 formed in the cover 45 of the gear casing. The plunger I24 is movable in a direction parallel to the axis of the cam 92 and is provided with a conical head I25 adapted to bear on the periphery of the cam. Within the socket I25 and back of the plunger I24 is a compression spring I21 tending to force the plunger outwardly and to hold the conical head I26 in engagement with the cam. The plunger I24 is positioned so that it will engage arising surface on one of the lobes of the cam when the lever 94 is in engagement with a receding surface, and will engage a receding surface of the cam when the lever 94 is in engagement with a rising surface.

As the cam rotates in a clockwise direction, as shown in Fig. 3, the rising surface of one of the lobes of the cam will cause the plunger I24 to move inwardly of the socket I25 and thus progressivel compress the spring I21. During this period of time, the lever 94 engages a receding portion of the cam to permit the shoe 23 to move away from the roll. Since the spring 34 is at this time tending to assist the motor, the compression of the spring I2! will absorb energy and thus provide the desired braking action.

When the shoe is next shifted toward the roll, the lever as is in contact with a rising. portion of one of the lobes of the cam, and in the final part of the movement the motor also functions to compress the spring 34. During this period of time, the plunger I24 is in contact with a receding portion of one of the cam lobes, and the energy previously stored in the spring I21 tends to drive the cam forwardly through a camming action between the conical head I26 and the periphery of the cam. Thus the energy previously stored in the spring I27 when the load on the motor was relatively light is now utilized to assist the motor when the load on the motor is relatively heavy. The effect of the spring 34 on the drive mechanism is therefore counterbalanced, and the peak load on the motor is materially reduced. since when the spring 34 is tending to retard the drive mechanism, the plunger I24 is tending to advance the drive mechanism. In practical operation, it is found that a very considerably smaller motor may be used in the machine by virtue of the compensating effect of the plunger [26 and its function of reducing the peak load on the motor.

The lobes es of the cam 92 are shaped to minimize the effect of the spring 34 on the driving mechanism and to store energy in the spring I2I when the spring 34 tends to overdrive. It will be noted that each lobe 93 has a rising portion comprising a sharply sloping portion IIB (see Fig. followed by a much more gradually sloping portion H9, while the receding portion has a slope, indicated at I 28, which is substantially constant. The sharply sloping portion I I8 serves to effect the first part of the movement of the shoe toward the roll before the spring 34 is compressed and the load is consequently light. The gradually sloping portion I I9 acts when the spring 34 is being compressed and thus provides greater power to perform this function. During both of these movements, the plunger I24 is acting on the constantly sloping receding portion I28 of the adjacent lobe to exert a constant driving force.

During the first part of the time when the re ceding portion I 28 is acting to move the shoe away from the roll, the spring 34 tends to overdrive the mechanism. At such time, the sharply sloping portion H8 of the cam is rapidly placing the spring I21 of the plunger I24 under compression so that the major portion of the energy stored in the spring I2! is stored during the time when the spring 34 tends to effect such overdrive. After the spring 34 is relieved of its pressure and no longer tends to overdrive the drive mechanism; the plunger I24 is acted upon by the gradually sloping portion H9. Thus, the effect of the spring 34 is minimized by the shape of the cam, and energy is stored in and expended by the spring I21 to the greatest advantage.

Control of the machine The shifting of the shoe is, of course, under the control of the operator, and the rotation of the roll is controlled as an incident to the shifting movement of the shoe. To further reduce the load on the motor, the roll or operating clutch 60 is adapted to be engaged only-after the shoe has substantially completed its movement toward the roll and to be disengaged before the shoe is moved away from the roll so that the motor will not be called upon to drive the roll during such time that its power is being utilized in shifting the shoe.

As heretofore described, the roll clutch 60, when the roll is operating, is adapted to be shifted out of engagement by the bell crank 14. To effect such shifting movement manually, the rock shaft I2I, which extends through the tubular member 96, carries adjacent its outer end an operating arm I30 (see Figs. 3, 5, 6 and 7). The operating arm I353 is provided with two angularly spaced actuatingportions or fingers, one of which, indicated at I3I, is adapted to engage the adjacent arm of the bell crank 74 to so swing the bell crank as to force the clutch 6% out of engagement with the gear fit. The rock shaft I2I extends through the tubular member 96 and to a point outside of the gear casing cover 45 but within the head 2I. The outer end of the rock shaft I2I is connected to manually operable means, hereinafter described, which is so constructed that the rock shaft and operating arm I39 may be rocked manually in a clockwise direction, as viewed in Figs. 3 and 6. To return the arm I30 to its original position, a torsion spring I29 (see Fig. 4) is mounted on the shaft I2I with one end secured to the shaft and the other end bearing against the adjacent portion of gear casing cover 45.

The actuating finger I 3| of the arm I30 is so positioned that it engages the bell crank I4 immediately upon the start of the rocking movement of the shaft I 2i. The roll clutch 6!! is thereby disengaged during the first part of the movement of the operating arm I353.

Further rocking movement of the shaft I2I thereafter causes actuation of the shoe shifting mechanism. For this purpose the operating arm I3!) is provided with a second actuating finger I32 movable parallel to the face of the disengaging member H5 and engageable with a cam surface I33 formed on the disengaging member II5 intermediate its ends. The disengaging member H5, in its preferred form, comprises a strip of metal bent so that it may extend parallel and closely adjacent to the operating arm I38, and the cam surface IE3 is provided merely by forming a bulge in the strip of metal. The second operating finger I32 is so positioned relative to the first operating finger I3I that the finger I32 engages the cam surface I33 after the roll clutch has been shifted. The disengaging member I I will thereby be shifted laterally out of the path of the clutch finger 86 of the shoe shifting mechanism to permit engagement thereof with the driving member 83 for effecting the shifting movement of the shoe away from the roll.

When the shoe is positioned. away from the roll, means is provided for holding the roll clutch 60 disengaged so that the operating arm will not have to be manually held in a position to stop the drive of the roll. To this end, the pivot pin 91 which connects the levers 94 and I38 is provided with an extension I34 projecting into the pathof movement of the bell crank M. When the shoe is away from the roll, the extension I34 engages the bell crank I4 so that the latter holds the roll clutch disengaged. The operating arm I33 may therefore be released to be returned to its origi nal position by the torsion spring 123, and the roll clutch will continue to be held disengaged.

Since the operating arm I30 is permitted to return to its original position immediately after being rocked to move the disengaging member out of the path of the finger 85, the disengaging member is shifted back into the path of the finger 86 by the spring I23. Such movement of the disengaging member occurs during the time when the finger 86 and the driven member 84 are making one revolution, or, in other words, when the cam 92 is moving through one eighth of a revolution. The disengaging member H5 will thereupon effect disengagement of the finger 86 from the driving member, and the shoe will remain in its position away from the roll.

To move the shoe toward the roll, the rock shaft IZI is again manually operated to rock the operating arm I30. The first actuating finger I3I does not, in this instance, affect the roll clutch 66, since the latter is held disengaged by the extension I34. However, the second actuating finger I32 of the operating arm I30 again forces the disengaging member H5 out of the path of the finger 86 to permit the latter to engage the driving member 83. Such engagement thereupon causes actuation of the cam 92 to move the shoe toward the roll. As the shoe moves toward the roll, the extension I34 is shifted by movement of the levers 94 and IE3, and the bell crank 74 permits the spring ID of the roll clutch to cause engagement of such clutch and start the roll.

In present-day ironing machines, it is of course desirable to be able to stop the rotation of the roll when the shoe is in operative relation therewith in order to utilize the machine for pressing. The present manual control provides for such method of operation of the machine without necessitating a separate control lever therefor. Thus, assume that the roll is rotating and the shoe is in operative relation thereto and it is desired to stop the roll to press the article being ironed. By rocking the rock shaft I2! through the first part of its movement, the roll clutch 60 may be disengaged as described above. However, the operating arm I 38 need not be moved through its full range so that the shoe control clutch will not be actuated. Thus the shoe will remain in operative relation to the roll but the roll will be stopped. Such stoppage of the roll may be continued so long as the rock shaft I2I is held in its partially rocked position. Release of the rock shaft I2I so that it may be returned to its original position by the torsion spring I29 again starts the rotation of the roll since the roll clutch 65) will again become engaged. However, if it is desired to shift the shoe away from the roll at the conclusion of the pressing, the rock shaft I2! may then be operated to the full extent of its movement for withdrawing the shoe from the roll.

If it is desired to shift the shoe toward the roll and immediately utilize the machine for pressing without ever starting the roll, the rock shaft I2I is first moved through its full range of movement to eifect shifting of the shoe. However, instead of completely releasing the rock shaft so that it would move back to its original position, it is permitted to turn only part way toward the original position, far enough so that the second actuating finger I32 is clear of the cam surface I33 but the first actuating finger i3i is not shifted far enough to permit engagement of the clutch 63. Thus the shoe will be shifted toward the roll but the shoe shifting clutch will be held out of engagement.

One of the principal features of the machine is the ease with which it may be controlled and the fact that it may be controlled in many different ways, depending upon the convenience of the operator. The rock shaft IiZI at its outer end but Within the head 2| is bent to provide a rearwardly extending arm I35 (see Figs. 1, 2, 4 and 5). Connected to the outer end of the arm I35 is a-link I33 extending downwardly within the head 2 l.

The lower end of the link I33 is adapted to be connected to a manually operable member provided with means extending externally of the machine, which may be placed in a number of different positions to suit the convenience of the operator. For this purpose, the lower end of the link is connected to a triangularly shaped lever I3l rigid with a tubular member I rotatably mounted in the lower part of the head 2| and extending from front to rear therein. The tubular member Hi6] is provided with a round interior portion Mi for the major portion of its length, but at its rear end is provided with a non-circular socket N52. The tubular member Hi6) is aligned with an aperture in the front wall of the head 2! and a hand lever I43 is adapted to be inserted through such aperture and into the tubular member Mil. The hand lever is dimensioned so that it fits snugly within the round interior portion I iI of the tubular member I46 and is provided on its rear end with a non-circular portion adapted to fit into the socket M2. Actuation of the hand lever thus will rotate the tubular member I iil to move the link I36 downwardly and thus actuate the rock shaft I2I.

The non-circular socket It? is provided with some regular polygonal form so that the hand lever hi3 may be inserted therein in a number of angularly different positions. In the present instance, the socket M2 and the cooperating portion of the hand lever are hexagonal in shape. Thus the hand lever Hi3 maybe inserted in the socket I42 in such a manner that the hand lever extends generally upward as shown in the full line position in Fig. 1. The outer end of the hand lever is bent at a slight angle to the main portion thereof and is provided with a hand gripping portion Hi l. When the hand lever is in its full line position shown in Fig. l, the hand gripping portion is in a convenient location so that it may be readily operated without too great a movement of the operators hand when ironing small Q tion of the roll and in front thereof.

articles, suchas towels, handkerchiefs or the like; However, when ironing larger articles, such as sheets, tablecloths, etc., such articles frequently overhang both ends of the machine. The hand lever I43 may then be inserted in the socket M2 in a position 60 removed from its upright position and to the right thereof, as indicated at I45 in Fig. l. The hand lever thus extends outwardly fromtheright end of the machine and, away from the ironing elements, andmay' be readily grasped by the operator when ironing such large articles.

When ironing shirts or other articles where certain portions of the article are ironed while the main portion may be held by the operator, it is desirable to so place the hand lever I43 that it may be operated merely by a nudge of the operators elbow. To permit such manipulation of the hand lever, it may be so inserted into the tubular member M that it extends at a position 60 to the left of its upright position, as indicated-at I46, so that the handle portion I44 extends substantially parallel to the lower por- Thus the operator while handling an articleat the top of theroll may readily operate the hand lever with her elbow.

The hand crank I43 may also be inserted in the tubular member l iil so that it can be actuated by the operators knee. Since the ironing machine shown herein is of the type adapted to be'placed on the top of a table, the hand lever M3 is so dimensioned that it will extend forwardly-from the-machine a substantial distance. Thus when inserted in a position, shown at I41, at" 120 to the left of the vertical position, the level" may extend downwardly past the front edge of the table supporting the machine, and the handle portion I44 will be in a convenient location extending vertically downward for ac tuation by the operators' knee. Such position is frequently used by the operator when seated in front of the machine, and permits free use of her hands for manipulation of the articles being ironed.

It may. also be desirable to construct the machine for foot operation. To-provide for this, the triangular'lever I3? is positioned so that one corner" thereof extends downwardly into the base 20', as shown in Fig. l. The lower corner of the lever I31 is bent to provide a lug I49 having an aperture: I501 to which a cable or wire I5I may extend, The wire is adapted to extend out the end of the base 20' and a flexible casing surrounding the wire may be detachably secured at one end within the base. The wire I5I', being flexible, may be extended downwardly to any desired position on the floor and be provided there with a suitable treadle (not shown) for operating it. Thelwire I 51 and treadle may be made as a separate attachment for the machine, to be sold as an accessory therefor, the machinemerely being provided with an aperture in the base through which the end of the wire and its casing may be inserted.

Operation o) the machine the roi'lis permitted since the roll clutch Si) is then disengaged, and the force necessary to rotate the roll is only such as is required to rotate the roll gear 62,-the pinion 3i and the stub shaft 57. The friction of these parts, however, is such that the rollwill not be too freely rotated, thus notmaking it difficult to hold the roll in the desired position before starting.

With the article in place on the roll, the operator actuatesthe hand lever H33 in a counter clockwise direction, as viewed in Fig. i, which swings the triangular lever I37 to rock theshaft I2I in the desired direction. Movement of the rock shaft I2I causes rocking movement of the operating arm I36 within the gear casing. Since the roll clutch 60 is held in disengaged position by the extension I34 of the pin 91 at this time, the roll clutch will be unaffected by movement of the operating arm I311. However, movement of the operating arm through its entire range causes the actuating finger I32 to cam the dis engaging member I I5 out of engagement. with the end I I4 of the clutch finger 86. The torsion spring It? will then swing the finger 8%: about the pin I05 and cause the tooth I66 to enter the notch inthe driving member 83. Full driving engagement by the straight rear side INS of the notch in the driving member will thereupon cause rotation of the driven member 84'. During the first part of suchdriving movement, the finger 88 will be shifted on the pin I05 so that the latter is located in the outer end of the slot I2d' in the finger, as shown in Fig. 6.

Rotation of the driven member 84 effects rotation of the shaft 82 and the pinion 8 7 to drive the gear 911* and the shaft 9| carrying the cam 92'. Since the gear ratio'between the pinion 8 1 and gear is 8 to 1, the cam will be rotated through a distance equal to one half the. angularity of one of its lobes 93.

Such movement of the cam causes the rounded end 95 of the lever 94 to be swung outwardly, as viewed in Fig. 3, by therising portion of the lobe, and the lever 94* will thereby be swung in a counterclockwise direction. Movement of the lever 94 through its connection by the pin 9! with the shaft I96- will' cause the latter, together with the rockshaft IIlI- and the second intermediate lever I 02, to swing in a clockwise direction. Such.- movement obviously through the links I03, lever 31, rock shaft 2! and lever arm 26 will cause the shoe to be moved toward the roll. Theinitial portion of such movement merely serves to effect the movement of the shoe.

However, during the latter part of the movement, when the shoecontacts the article to be ironed on the roll, the spring 34 will be compressed to providethe desired ironing pressure Such compression of the spring 34 would add materially to the load on the motor but it is, however, counter bal'anced by the effect of the energy storing device comprising the plunger I24 and the compression spring I27. In the previous movement of the shoe away from the roll the spring I21 was compressed so that during the present movement of the shoe toward-the roll; the plunger I24 may now utilize the'pressure of the spring I21 to assist in moving the cam forwardly by a camming action of the head IZ-B of the plunger on the periphery of the cam, the head I2B during this period being in contact with a receding portion of one of the lobes of the cam. Thus the load on the motor is materially reduced during this period of operation.

Movement ofthe pin 91 during such operation shifts the extension I3 I -thereofout of the way of the bell crank I4 so that the latter permits the roll clutch 60 to become engaged. However, such engagement of the roll clutch will not occur until the movement of the shoe toward the roll is substantially completed, since the extension I34 first has to move out of the way of the bell crank l4 and the spring I of the roll clutch has to cause the flange st to fully engage with the driving pins 01 in the constantly rotating gear 56. The slight delay occurring in the movement of these various parts prior to full engagement of the roll clutch is sufficient to permit the shoe to move substantially into its operative position.

Should the operator desire to utilize the machine for pressing at this time without ever permitting the roll to start its rotation, the hand lever I43 is not permitted to move back completely to its original position but just sufficiently to swing the second actuating finger I82 out of engagement with the disengaging member II5. In such position of the operating arm I30, the first actuating finger I3I will hold the roll clutch disengaged. However, the disengaging member H is at such time permitted to return to its normal position in the path of the end H4 of the finger 80 so that it will effect disengagement of the tooth I00 from the driving member 83 after one revolution of the finger.

When the finger 86 is so disengaged, the driven member 84 will stop. The finger 86, however, is shifted entirely clear of the driving member 83 so that no clicking noise will occur, since the torsion spring I0'I will cause the finger 86 to pivot about its end II4 to the extent permitted by the elongation of the slot I20. In other words, the finger will swing so that the pin I05 occupies the inner end of the slot I and the tooth I05 will be spaced a substantial distance from the driving member 83 so that the teeth of the latter cannot click against the tooth I00 during relative rotation.

If, after pressing the article, it is desired to iron it without moving the shoe away from the roll, all that need be done is to release the hand lever I43 to permit it to swing back to its original position. By so doing, the first actuating finger I3I will swing out of engagement with the bell crank I4 and permit the roll clutch 60 to en age. Such movement in no way affects the disengaging member II5 so that the shoe will remain in operative relation with the roll.

Should the operator first desire to iron a portion of the article and then press, the operating lever I43 when first actuated is permitted to return to its original position. Theshoe is shifted towards the roll as described above and after such shifting movement takes place, the roll clutch 60 will engage. When it comes to the point where the operator wishes to use the machine for pressing, she merely moves the hand lever I43 a short distance, sufficient to cause the first actuating finger I3I to swing the bell crank and disengage the roll clutch 60. However, by such short movement the disengaging member H5 is not shifted so that the shoe will remain in operative relation with the roll and pressing may be ef- .fected.

' face I33 to shift the disengaging member H5 out of engagement with the end I I4 of the finger Such movement 8t. The driven member 84 will thereupon be rotated through one revolution to cause the cam to move through one eighth of a revolution. During such movement, the rounded end of the lever 94 is in engagement with a receding portion of the cam, and the pressure of the spring 34 as well as the weight of the shoe and its supporting arm 20 tend to swing the shoe away from the roll. At the same time, the head I26 on the plunger I24 is in contact with a rising portion of one of the lobes of the cam, and the plunger I24 is thereby being shifted to compress the spring I21. Compression of the spring I21 counterbalances the assisting or driving effect of the spring 34, and energy will thereby be stored in the sprin I2'I for use during the next movement of the shoe toward the roll.

The hand lever I43 when actuated for causing movement of the shoe away from the roll is immediately released to swing back to its original position so that the clutch disengaging member will thereupon be moved into the path of the end II4 of the finger 86 to disengage the latter after one revolution. As the levers 94 and I00 swing to move the shoe away from the roll, the extension I34 on the pin 9'5 is moved into position to hold the bell crank for retaining the clutch 60 in its disengaged position. Thus when the machine is idle with the shoe moved out of operative relation with the roll, the roll is held stationary.

From the foregoing description, it will be apparent that I have provided a novel ironing machine having a pair of ironing elements, at least one of which is a roll, and one of which is movable toward and from the other by power actuated means driven by the motor for driving the roll. The machine is of such capacity as to be suitable for ordinary domestic use, and the mechanism for shifting the movable element as well as all the mechanism of the machine is of such character that a relatively small motor may be employed to serve both driving functions. Thus the machine has a capacity equal to that of much heavier machines, but its total weight is such, chiefly due to the smaller motor, that it may be constructed in the form of a portable machine. The chief reason why a relatively smaller motor may be employed is because of the .fact that the energy storing device comprising the plunger I24 is adapted to absorb energy from the motor during that portion of the operating cycle of the machine when the spring 34 in the shoe supporting arm tends to overdrive the driving mechanism. The energy so stored in the spring l2! coaoting with the plunger I 24 is returned to the driving mechanism, by tending to drive the actuating cam 92 forwardly, during the time when the load on the motor would otherwise be at a peak, that is, when the shoe is being moved toward the roll and the spring 34 is being compressed.

Other contributing features permitting the use of a small motor are the fact that the roll drive is so arranged that there is very little frictional load from such drive on the motor during the time when the roll is idle, since the roll clutch 60 is placed relatively near the motor in the gear reduction connecting the motor with the roll. Further, the gearing connecting the shoe actuating cam 92 with the motor is such that the cam has to be moved only through an eighth of a turn to accomplish this movement. Another contributing feature is that the effective leverage of the intermediate lever I00 is increased by virtue of the elongated slot I04 during the time when 21 the shoe is moving toward the roll and the spring 34 is being compressed.

The mechanism for driving the roll and shifting the shoe is compact in construction and thus may be enclosed within a gear casing of such dimension that it may be positioned within the roll. The roll supporting head may therefore be relatively small and not cumbersome. Such compactness of the gearing is accomplished through a number of factors which, taken together, give the desired result. Thus it will be noted that the shoe shifting clutch is of the one revolution type, as distinguished from the half revolution type heretofore commonly used, so that the disengaging means for the clutch may be of very'simple form. The disengaging member H5 as well as the operating arm 1'30 and the lever arm 94 are all mounted on the same axis so that part of the compactness is thereby obtained. Both the roll clutch 6D and the shoe shifting clutch operate at such speed that the load thereon is held to a minimum and disengagement thereof may be readily accomplished. The shoe shifting clutch comprising the finger 86 and the driving member 83 are so related that when the finger 86 is disengaged, it is shifted entirely clear of the driving member 83 by means of the torsion spring Iil'l so that they avoid all chance of clicking against each other after such disengagement.

The control of the machine is particularly convenient. Thus the same lever which is used for effecting the shifting movement of the shoe and for starting and stopping the roll as an incident thereto is also used to stop the roll' when it is desired to use the machine for pressing. The hand lever M3 by which the machine is controlled may be adjusted into a variety of positions to suit the convenience of the operator. Thu it has two positions for hand operation, one position for elbow operation, and still another position for knee operation. The machine is also constructed so that a foot control device may be readily connected thereto.

What. is claimed is:

1. In an ironing machine, the combination of a. pair of ironing elements, onebeing shiftable toward, and from the. other, spring means tending to prevent separation of said elementswhen said elements are in operative relation, mechanism for effecting the shifting movement of the one element, a motor for driving said mechanism, said mechanism including gearing connected to the shiitable element and having operatively connected therewith rotary means for shifting the shiftable element toward and from the other element, and an energy storing device in operative, engagement withv said rotary means to absorb. energy therefrom and thereby provide a braking action onsaid mechanism during the separating movement ofi said elements, said device coacting with said. rotary means to return said energy thereto to augment the power of the motor when said mechanism effects movement of the one element toward the other.

2-. In an ironing machine, the combination of a pair of ironing elements, one being shiftable toward and from the other, power driven mechanismfor effecting shifting movement of the one element, resilient means. for exerting pressure of one element. toward the other when the two are in operative relation, said mechanism thereby placing said mean underpressure. when. shifting the; one; element. toward the other. andsaid pressure tending to assist said mechanism: in shifting the one element away from the other, said mechanism including gearing connected to the shiftable element and having operatively con nected therewith rotary means for shifting the shiftable element toward and from the other element, and. a device in operative engagement with said rotary mean and actuated by said rotary means to oppose said mechanism in shifting the one element away from the other and acting on said rotary means to assist said mechanism in shifting the one element toward the other.

3. In an ironing machine the combination of a pair of ironing elements, one being shiftabl'e toward and from the other, the other element being a roll, drive means for said roll including a spring actuated clutch, power driven mechanism comprising gearing connected to the one element and including rotary means for effecting shifting movement of the one element, resilient means for exerting pressure of one element toward the other when the two elements are in operative relation, and means in operative engagement with said rotary means for absorbing energy from said mechanism during part of its movement and for returning such energy to said mechanism during another part of such movement,,said two means acting oppositely on said mechanism when said mechanism effects shifting'movement of the one element to substantially equalize the power load on said mechanism for all parts of its movement.

4. In an ironing machine, the combination of a rotatably driven roll, a cooperating shoe, power driven mechanism for rotating the roll including a clutch and resilient mean for engaging the clutch, power driven mechanism including rotary means having an operative connection with said shoe for shifting the shoe toward and from the roll, a second resilient means cooperating with said shoe shifting mechanism for causing. the shoe to exert pressure toward the roll when the shoe and roll are in operative relation, said sec- 0nd resilient means thereby opposing said mechanism when the latter shifts the shoe toward the roll and assisting said mechanism when it shifts the shoe away from the roll, and an energy storing device in operative engagement with said rotary means for absorbing energy by opposing said shoe shifting mechanism when it shifts the shoe away from the roll and for returning said energy to said mechanism when the latter Shifts roll and assisting said mechanism when it shifts the shoe away from the roll, and a second resilient means in operative engagement with said rotary means for counterbalancing the action of said first-mentioned means on said mechanism.

6. In an ironing machine, the combination of a pair of ironing elements, power driven mechanism including gearing connected to one of said elements and having operatively connected therewith a rotatable cam for shifting said one element: toward and. from. the other element, resilient means for exerting pressure of one of said elements toward the other when the two elements are in operative relation, and a second resilient means in operative engagement with said cam and adapted to be placed under pressure by said cam during a part of its movement and for assisting in the actuation of said cam during another part of its movement, said two resilient means acting oppositely on said mechanism when said mechanism effects shifting movement of the one element to substantially equalize the power load on said mechanism for all parts of its movement.

7. In an ironing machine, the combination of a pair of ironing elements, power driven mechanism for shifting one of said elements toward and from the other including gearing connected to said one element and having operatively connected therewith a cam for shifting said one element toward and from the other element, resilient means for causing one element to exert pressure toward the other element when said elements are in operative relation, said resilient means thereby opposing said mechanism in moving the one element toward the other and assisting said mechanism in moving the one element away from the other, and a spring pressed device in operative engagement with said cam and adapted to be placed under pressure by said cam when said mechanism shifts the one element away from the other and to utilize said pressure to assist in the actuation of said cam when said mechanism shifts the one element toward the other.

8. In an ironing machine, the combination of a pair of ironing elements, power driven mechanism for shifting one of said elements toward and from the other including gearing connected to said one element and having operatively connected therewith a rotatable cam for effecting actuation of the one element, resilient means adapted to be placed under pressure when the one element is shifted toward the other, said resilient means thereby opposing the rotation of the cam when the one element is shifted toward the other and tending to efiect rotation of the cam when the one element is moved away from the other, and a second resilient means in operative engagement with said cam to counterbalance the action of said first-mentioned resilient means on said cam.

9. In an ironing machine, the combination of a pair of ironing elements, power driven mechanism for shifting one of said elements toward and from the other including gearing connected to said one element and having operatively connected therewith a rotatably driven cam having a plurality of rising portions for shifting the one element toward the other and a plurality of receding portions for shifting the one element away from the other, resilient means for exerting pressure of one element toward the other when the two elements are in operative relation,

said resilient means opposing the rotation of the cam when one of said rising portions thereof is functioning and assisting the rotation of the cam when one of said receding portions thereof is functioning, and a second resilient means in operative engagement with said cam and acting on one of said receding portions of the cam when one of said rising portions is functioning to shift the one element toward the other and acting on one of said rising portions of the cam when one of said receding portions is functioning to shift the one element away from the other.

10. In an ironing machine. the combination of a pair of ironing elements, one being shiftable toward and from the other, a rotatably driven cam having a plurality of radially extending lobes with each lobe having a rising portion and a receding portion, a cam follower in peripheral engagement with said cam and provided with a connection for shifting the one element toward and from the other, said connection including resilient means for exerting pressure of one element toward the other when the two elements are placed in operative relation through actuation of said cam, said resilient means thereby opposing rotation of said cam when the one element is moving toward the other and assisting rotation of the cam when the one element is moving away from the other, and a spring pressed member in operative engagement with said cam and adapted to be placed under compression by said rising portions and to utilize such pressure to assist rotation of the cam when in engagement with said receding portions, said spring pressed member thereby counterbalancing the action of said resilient means on said cam.

11. In an ironing machine, the combination of a pair of ironing elements, one being shiftable toward and from the other, a power driven cam having a plurality of radially extending lobes each comprising a rising portion and a receding portion, a cam follower in peripheral engagement with said cam for shifting the one element toward and from the other by said rising portions and said receding portions, resilient means for causing one element to exert pressure toward the other when the two are in operative relation, a spring pressed plunger movable axially of said cam and having a bevelled surface contacting the periphery thereof, said plunger being positioned to be in contact with a rising portion when said cam follower is in contact with a receding portion and to be in contact with a receding portion when said follower is in contact with a rising portion and thereby counterbalancing the action of said resilient means on said cam.

12. In an ironing machine comprising a pair of relatively shiftable ironing elements and resilient means for yieldably urging one of said elements toward the other when the two.are in operative relation, the combination of a gear casing, power driven gearing within said casing including a rotatable cam and a cam follower, means actuated by said cam follower for shifting one of said elements toward and from the other, said resilient means tending to retard and advance said cam when the latter effects movement of the one element toward and from the other element, said gear casing having a socket adjacent to and extending axially of said cam. a compression spring in said socket, and a plunger extending into said socket and engaging said cam, said plunger tending to advance and retard said cam when the latter effects movement of the one element toward and from the other element and thereby counterbalance the effect of said resilient means on said cam.

13. In an ironing machine, the combination of a pair of ironing elements, one shiftable toward and from the other, resilient means for yieldably urging one of said elements toward the other when the two are in operative relation, mechanism for shifting the one element toward and from the other, a motor for driving said mechanism, said resilient means tending to increase the load on said motor during the shifting of the one element toward the other and to decrease the load during the shifting of the one element away :from the other, said mechanism including gearing connected to the shiftable element and having operatively connected therewith rotary means .for shifting the shiftable element toward and from the other element, and energy storing means in operative engagement with said rotary means and adapted to store energy when the motor load is decreased by said resilient means'and to utilize said energy to .assist th motor when said resilient means tends to increase the :motorlload.

14. In an ironing machinecomprising a pair of relatively shiftable ironing elements, the combination of resilient means for yieldably urging one of said elements toward the other when the two are in operative relation, power driven mechanism including gearing'connected to the shiftable element and having operatively connected therewith'rotar-y means forshifting the shiftable element toward and from the other element, said resilient means tending to retard and advance the movement of the one element toward and from theother, and an energy storing device in operative engagement with said rotary means and tending to advance and retard the movement of the one elementtoward and from the other.

15. In an ironing machine comprising a pair of relatively shiftab'le ironing elements, the combination of resilient means for yieldably urging one of said elements toward the other-when the two are in operative relation, power driven mechanism including a cam having a plurality of lobes for shifting one of said elements toward and from the other, a cam follower cooperating with said cam and connected with the shiftable element, and an energy storing device cooperating with said cam to counterbalance the .efiect of said resilientmeans on said cam acting through said cam follower, said cam follower and said device being relatively positioned to engage opposite points on the lobes.

16. In an ironing machinecomprising a pair of relatively shiftable ironing elements, the combination of resilient means for yieldably urging one of said elements toward the other when the two are in operative relation, a motor, a cam having cam surfaces for shifting said one element toward and from the other, gearing connecting said cam with said motor, a cam follower engaging said cam surfaces and connected with the shiftable element, said cam having a plurality of lobes to eiiect movement of the shiftable element and thereby being operable at a relatively slow speed to reduce the load on the motor, and an energy storing device engaging said cam surfaces and acting on said cam to counterbalance the effect of said resilient means thereon and thereby reduce the load on the motor.

17. In an ironing machine comprising a pair of relatively shiftable ironing elements, the combination of power driven mechanism for shifting one of said elements toward and from the other including an actuating cam comprising a rising portion having sharply sloping and gradually sloping parts, and a receding portion, resilient means for yieldably urging one of said elements toward the other when the two are in operative relation and tending to overdrive said mechanism during the time when the first part of said receding portion is functioning, and energy absorbing means engaged by said sharply sloping part when said resilient means tends to overdrive said mechanism to absorb the major portion of the energy during such time.

18. In an ironing machine comprising a pair of relatively shiftable ironing elements, the combination of power driven mechanism including gearing connected to one of said elements and having rotary means for shifting said one element toward and from the other, resilient means for yieldahly urging one of saidelements toward the other when the two are in operative relation and tending .to overdrive said mechanism when the one element is moved away from the other, a spring, a plunger engaging said spring and in :operative engagement with said rotary means and shiftable thereby to place said spring under I'load progressively throughout the movement of the one :element away from the other to prevent said overdrive.

19. In an ironing machine comprising a :pair of :relatively shiftable ironing elements, the combination of power driven mechanism including gearing adapted to be connected to one of said elements and having operatively connected therewith rotary means for shifting said one element toward and from the other,.resi1ient means for yieldaoly urging one of said elements toward the other when the two are in operative relation and thereby tending to oppose movement of the one element toward the other, and spring pressed means in operative engagement with said rotary means and adapted to assist said mechanism during movement of the one element toward the other.

20. In an ironing mechanism comprising a under pressure when said gradually sloping part is functioning, andspring pressed means in operative engagement with said cam and adapted to exert a substantially constant driving force on said cam during the entire time when said rising portion is functioning.

21. In an ironing machine, the combination of a pair of relatively shiftable ironing elements, resilient means for exerting pressure of one element against the other when the two are in operative relation, and power driven mechanism for shifting one of said elements toward the other and thereby placing said resilientmeans under pressure, said mechanism including a power operated lever provided with a pin, and an intermediate lever connected to the shiftable element and having a slot to receive said pin extending lengthwise of said intermediate lever, said levers being adapted to move away from an aligned position in shifting the one element toward the other whereby the effective length of said intermediate lever will be increased by the movement of said pin in said slot to increase the leverage thereof in placing said resilient means under pressure.

22. In an ironing machine, the combination of a pair of relatively shiftable ironing elements, one being a roll, power driven mechanism for rotating the roll, a roll clutch for connecting said mechanism with the roll, a cam for shifting one of said elements toward and from the other, a second clutch for connecting said cam with said mechanism, linkage connecting said cam with the shiftable element, a clutch controlling mem her for said second clutch, a shiftin member for said roll clutch, manually operable means engaging said shifting member for actuating said shifting member to disengage the roll clutch and engaging said clutch controlling member for causing engagement of said second clutch, and an abutment carried by said linkage for holding said shifting member in clutch releasing position when the one element is away from the other.

23. In an ironing machine, the combination of a pair of relatively shiftable ironing elements, one being a roll, power driven mechanism for rotating the roll, a roll clutch for connecting said mechanism with the roll, a bell crank having one arm engaging said r011 clutch to effect shifting thereof, a cam for shifting one of said elements toward and from the other, a second clutch for connecting said cam with said mechanism, linkage connecting said cam with the shiftable element, a manually operable member engageable with the other arm of said bell crank to disengage the roll clutch, said manually operable member also being arranged to cause engagement of said second clutch, and an abut ment carried by said linkage and engageable with said other arm of the bell crank for holding said bell crank in clutch releasing position when the one element is away from the other.

24. In an ironing machine, the combination of a pair of relatively shiftable ironing elements, one being a roll, power driven mechanism for rotating the roll and shifting one of said elements toward and from the other, a roll clutch for connecting said mechanism with the roll, a shifting member for said roll clutch, a second clutch for effecting shifting movement of the one element, manually operable means for actuating said shifting member to disengage the roll clutch and for causing engagement of said second clutch, and linkage connecting said mechanism with the shiftable element including a pair of levers, and a pin connecting said levers,

WILLIAM H. BRADLEY.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,392,720 Synck et al. Oct. 4, 1921 1,647,642 Ledbetter Nov. 1, 1927 1,656,664 Daly Jan. 17, 1928 1,675,444 Blando July 3, 1928 1,690,431 Pierce Nov. 6, 1928 1,717,890 Pauly June 18, 1929 1,834,082 Ballard et al Dec. 1, 1931 1,921,301 Peter et a1 Aug. 8, 1933 1,946,807 Neighbour Feb. 13, 1934 1,970,511 Foley Aug. 14, 1934 2,060,256 Smith, Jr Nov. 10, 1936 2,061,275 Hume Nov. 17, 1936 2,062,989 Castricone Dec. 1, 1936 2,083,092 Richer June 8 ,1937 2,083,505 Ringer June 8, 1937 2,136,541 Carson Nov. 15, 1938 2,136,722 McCabe Nov. 15, 1938 2,192,185 Dunham Mar. 5, 1940 2,224,013 Conterman Dec. 3, 1940 2,230,060 Jensen Jan. 28, 1941 2,247,149 Castricone June 24, 1941 2,247,803 Dunham July 1, 1941 2,253,964 Wardwell, Jr Aug. 26, 1941 2,259,062 Castricone Oct. 14, 1941 2,267,467 Johnson Dec. 23, 1941 2,302,662 Dyer Nov. 24, 1942 2,358,824 Peters Sept. 26, 1944 FOREIGN PATENTS Number Country Date 173,239 Great Britain Dec. 21, 1921 

